DE112015000158B4 - Motor oil supply device - Google Patents

Abstract

An engine oil supply apparatus comprising: a cylinder block (5) including a plurality of journal-bearing wall portions (51A to 51E) aligned in a cylinder bank direction and supporting a crankpin (41A to 41E) of a crankshaft (12) and a cylinder (8), respectively; communicating between the juxtaposed journal-bearing wall sections (51A to 51E) formed crank chamber (53); a shaft-supporting profile (52A to 52E) provided on the journal-bearing wall portion (51A to 51E) and supporting the crankpin (41A to 41E) of the crankshaft (12), and communicating with the journal-bearing wall portion (51A to 51E) ; and a nozzle mouthpiece (29a) fixed to a ceiling portion of the crank chamber (53) and supplying oil to a piston (9) which slides in the cylinder (8), the cylinder block (5) including a first oil supply path (65) directed toward Cylinder bank at a location on a side portion of the cylinder (8) extends in the direction of width, which is perpendicular to the cylinder bank direction; a branch oil path (68A, 68C, 68E) branched from the first oil supply path (65) at a position of the journal supporting wall portion (51A to 51E) and supplying oil to a crank bearing portion (50A to 50E) on which the crank journal (41A to 41E) is supported is; and a second oil supply path (66) extending in a direction of the cylinder bank at a location farther outside than the first oil supply path (65) in the width direction and supplying oil to the nozzle mouthpiece (29a), characterized in that the crankshaft (12 ) includes a plurality of crankpins (41A to 41E), and oil is supplied from a specific crankpin (41B, 41D) among the plurality of crankpins (41A to 41E) of the crankshaft (12) and a crank pin (43A to 43D) a passage (46A-46C, 47A-47C) formed inside the crankshaft (12) is defined, wherein the first oil supply path (65) and the second oil supply path (66) are respectively defined as a first sub-oil supply path and a second sub-oil supply path, and the branch oil path ( 68A, 68C, 68E) is defined as a first branch oil path (68A, 68C, 68E), the cylinder block (5) includes a main oil supply path (64) directed toward the cylinder bank at a position opposite to the first sub-oil supply path g (65) side, the cylinder (8) being the center and being supplied to the oil discharged from an oil pump (56), and a second branch oil path (68B, 68D) coming from the main oil supply path (64). branches off at a location of the journal-bearing wall portion (51B, 51D) and supplies oil to the crank bearing portion (50B, 50D) at which the specific journal (41B, 41D) is supported; the first sub-oil supply path (65) and the second sub-oil supply path (66) the first branch oil path (68A, 68C, 68E) supplies oil to the crank bearing portion (50A, 50C, 50E) of the crankpins (41A, 41C, 41E) other than the specific crankpin (41B, 41D) ,

Description

Technological background

The present invention relates to an engine oil supply device that supplies oil to corresponding parts of an engine of a motor vehicle or the like.

State of the art

The Japanese patent application JP H08-144 730 A discloses an engine oil supply apparatus in which a main passage and an oil nozzle passage connected to the main passage via a control valve are arranged in parallel to each other in a side portion in the cylinder block width direction (perpendicular to a cylinder bank direction). The oil supply device is configured to supply oil to a crankpin of a crankshaft via a supply path branching from the main passage and simultaneously supplying oil to a piston slide portion from an oil-jet nozzle connected to the oil-jet passage.

In an oil supply device such as that described above, it is desirable from a manufacturing and functional point of view that the respective channels formed in the cylinder block are rationally arranged. In addition, since the cylinder block is made by casting, it is recommended to suppress casting defects such as voids so that the yield can be improved.

From the US 2011/0 276 249 A1 An engine oil supply device according to the preamble of claim 1 is known.

The AT 4 340 E shows another engine oil supply device.

Summary of the invention

An object of the present invention is to provide an engine oil supply device which is rationally configured from the perspective of functions and manufacture of a cylinder block and to provide a corresponding method of manufacturing.

This object is achieved by an engine oil supply device according to claim 1 and a method according to claim 4.

The present invention relates to an engine oil supply apparatus comprising: a cylinder block including a plurality of wall portions supporting the journal, which are aligned in the cylinder bank width and each support a crankpin of a crankshaft and a cylinder communicating with a crank chamber disposed between the journal bearing, close to each other Wall sections is shaped; a shaft-supporting profile, which is arranged on the journal-bearing wall portion and carries the crank pin, which is in communication with the crankpin-bearing wall portion; and a nozzle mouth fixed to a ceiling portion of the crank chamber and injecting oil into a piston sliding in the cylinder, the cylinder block having a first oil supply path extending toward the cylinder bank at a position on a side portion of the cylinder perpendicular to the direction Cylinder bank width is; a branch oil path branching from the first oil supply path at a position of the journal supporting wall portion and feeding to a crank bearing portion Ö1 supporting the crank journal; and a second oil supply path that extends at a position toward the cylinder bank that is farther outward than the first oil supply path in the width direction, and that supplies oil to the nozzle tip.

list of figures

• [ 1 ] 1 shows in cross section a schematic configuration of a multi-cylinder engine in which an oil supply device according to the present invention is used.
• [ 2 ] 2 shows in vertical section a detailed structure of a bearing portion of a crankshaft.
• [ 3 ] 3 shows in vertical section a first bearing portion (a section along the line III-III in 2 ).
• [ 4 ] 4 shows in vertical section a second bearing portion (a section along the line IV-IV in 2 ).
• [ 5 ] 5 Fig. 10 is a schematic diagram of an entire configuration of an oil supply device.
• [ 6 ] 6 Fig. 12 is a schematic diagram of only one oil supply path (in the state where the oil supply path is shown diagonally from under a motor.)
• [ 7 ] 7 shows a cylinder block in plan view.
• [ 8th ] 8th shows a cylinder block from below.
• [ 9 ] 9 shows a cylinder block in cross section (along the line IX-IX in 8th ).
• [ 10 ] 10 shows a cylinder block in cross section (along the line XX in FIG 8th ).
• [ 11 ] 11 shows a cylinder block in lateral view.
• [ 12 ] 12 shows a diagram of the characteristics of a first oil control valve.

Description of the embodiments

Hereinafter, a preferred embodiment of the present invention will be described in detail with reference to the accompanying drawings.

<Configuration of the motor>

1 shows a multi-cylinder engine 2 (hereinafter simply referred to as an engine 2) equipped with an oil supply device according to the present invention. The motor 2 is a four-cylinder in-line gasoline engine in which a first cylinder 1 up to a fourth cylinder 4 successively in a straight line in a direction perpendicular to a plane of the paper in 1 are arranged, and which is installed in a motor vehicle such as a car.

The motor 2 contains a vertically coupled camshaft cover 3 , a cylinder head 4 , a cylinder block 5 , a crankcase 6 , and an oil pan 7 (please refer 5 ). Four cylinder bores 8th are in cylinder block 5 shaped, and in each of the cylinder bores 8th is a piston 9 housed sliding. The piston 9 , the cylinder bore 8th and the cylinder head 4 form a combustion chamber 10 for every cylinder. Furthermore, every piston 9 with a connecting rod 11 to a crankshaft 12 coupled, rotating from cylinder block 5 and the like is stored.

An inlet opening 14 and an outlet opening 15 in the combustion chamber 10 are on the cylinder head 4 arranged, and an inlet valve 16 and an exhaust valve 17 , each one the inlet opening 14 and the outlet opening 15 open and close, are at the openings 14 and 15 attached.

The inlet valve 16 and the exhaust valve 17 are each inclined in one direction, in which the respective openings 14 and 15 over return springs 18 and 19 close (an upward direction in 1 ) and are configured to have the respective openings 14 and 15 open by passing through cam sections 20a and 21a at the outer edge regions of the camshafts 20 and 21 pressed down. In particular, with a rotation of the camshafts 20 and 21 , press the cam sections 20a and 21a, the cam followers 22a and 23a down to the approximately central parts of the pivot arms 22 and 23 are arranged, and the pivot arms 22 and 23 pivot with a vertex of a pivot mechanism of one at one end of the pivot arms 22 and 23 as a fulcrum-mounted hydraulic valve lash adjuster 24 (hereinafter referred to as the HLA)). According to the pivoting, other end portions of the swing arms 22 and 23 press the intake valve 16 and the exhaust valve 17 down against the bias of the return springs 18 and 19 , This opens the respective openings 14 and 15 ,

In the cylinder head 4 Parts are arranged on an inlet side and on an outlet side, respectively corresponding to the four cylinders with mounting holes 26 and 27, at which the HLA are inserted and fixed. In addition, the oil routes 75 and 76 , each with the mounting holes 26 and 27, the HLA 24 communicating on the inlet side and the exhaust side, in the cylinder head 4 formed so as to extend in a cylinder bank direction across the first to fourth cylinders. The oil ways 75 and 76 deliver oil (operating oil) to the swing mechanisms of the HLA 24 that in the mounting holes 26 and 27 attached, and the pivoting mechanisms of the HLA 24 automatically reset the valve clearance to zero, using the oil pressure (working pressure).

In the cylinder block 5 runs a main channel 64 / the main oil supply path according to the present invention) in cylinder bank direction in a side wall on a side (intake side) of the cylinder bore 8th in the direction of the width of the cylinder block 5 , and a pair of side channels 65 and 66 (corresponding to the first and second Nebenölzufuhrweg according to the present invention) at predetermined intervals in the width of the cylinder block 5 are aligned and each extend in the direction of the cylinder bank, lead in the direction of the cylinder bank in a side wall on another side (exhaust side) of the cylinder bore 8th towards the width of the cylinder block 5. The respective channels 64 to 66 are oil paths for the corresponding channels to be described in detail later 64 to 66 ,

An oil nozzle 28 for cooling the pistons, which are connected to the main duct 64 is communicating at one point under the main channel 64 arranged and with each piston 9 connected. An oil nozzle 29 for lubricating the pistons, with the secondary duct 66 communicates, is between secondary channels 65 and 66 is disposed at a position which is in the vicinity of a lower side of the sub-channel 66, on an outer side in the width direction of the cylinder block 5 lies and with each piston 9 is connected (see 7 and 8th ).

Between oil nozzles 28 and 29 points the oil nozzle 28 for cooling the pistons a nozzle tip 28a mounted at a position closer to the inlet side than the cylinder bore 8th on a ceiling surface of a crank chamber 53 , and the oil nozzle 28 is configured to provide oil (cooling oil) in a shower-like pattern to the predominantly central portion of a rear surface of the piston 9 out of the nozzle mouthpiece 28a inject. On the other hand, the oil nozzle 29 for lubrication of the pistons a nozzle mouthpiece 29a on, at a location on an outlet side of the cylinder bore 8th on the ceiling surface of the crank chamber 53 is attached, and the oil nozzle 29 is configured to handle oil (lubricating oil) at a tighter angle than oil nozzle 28 for cooling the pistons to a rear surface of the piston 9 from the nozzle mouthpiece 29a to inject. An aperture for the oil is in the base area of the piston 9 shaped, and from the nozzle mouthpiece 29a Sprayed oil becomes a sliding surface of the piston through this passage 9 guided.

In addition, the oil supply sections 30 and 31 over the corresponding camshafts 20 and 21 arranged. The oil supply sections 30 and 31 have nozzle mouthpieces 30a and 31a and are configured so that oil (lubricating oil) from the nozzle mouthpieces 30a and 31a in the cam portions 20a and 21a (the lubricated portions) on the camshafts 20 and 21 and on the contact portions between the pivot arms 22 and 23 and the cam followers 22a and 23a dripping, the one under the nozzle mouthpieces 30a and 31a are arranged. Further (not shown) is a hydraulically operated variable valve train mechanism (VVT) in the engine 2 installed and changes the opening and closing settings of the intake and exhaust valves 16 and 17 according to an operating condition of engine 2 ,

2 shows in vertical section a detailed structure of a bearing portion of the crankshaft described above 12 ,

In 2 Seen from left to right contains the crankshaft 12 a first pin (crank pin) 41A abutting a front end portion 12A of the crankshaft 12 , a second pin 41B between the first cylinder 1 and the second cylinder 2 , a third pin 41C between the second cylinder 2 and the third cylinder 3 , a fourth pin 41D between the third cylinder 3 and the fourth cylinder 4 and a fifth pin 41E adjacent to a rear end portion 12B the crankshaft 12 ,

A first pair of crank webs (crank weights) 42A and a first crank pin 43A are between the first pin 41A and second pin 41B, a second pair of crank webs 42B and a second crank pin 43B are between the second pin 41B and the third pin 41C arranged a third pair of crank arms 42C and a third crank pin 43C are between the third pin 41C and the fourth pin 41D arranged, and a fourth pair of crank webs 42D and a fourth crank pin 43D are between the fourth pin 41D and the fifth pin 41E arranged.

In addition, a first on piston 9 of the first cylinder 1 coupled connecting rod 11A from the first crank pin 43A stored, a second on pistons 9 of the second cylinder 2 coupled connecting rod 11B supported by the second crank pin 43B, a third piston 9 of the third cylinder 3 coupled connecting rod 11C from the third crank pin 43C stored, a fourth on the piston 9 of the fourth cylinder 4 coupled connecting rod 11D from the fourth crank pin 43D stored.

The cylinder block 5 has bearing sections which the five pins 41A to 41E to store. Specifically, the bearing portions include a first bearing portion 50A who made the first cones 41A stores, a second storage section 50B , the second pin 41B stores, a third storage section 50C , the third pin 41C stores, a fourth storage section 50D , the fourth pin 41D stores, and a fifth storage section 50E who made the fifth pin 41E outsourced. In the present example, the bearing sections correspond 50A to 50E the crank bearing portions according to the present invention.

The respective storage sections 50A to 50E contain cylindrical bearing plates 44A to 44E (first bearing plate 44A to fifth bearing plate 44E ), opposite the outer edge surfaces of the pins 4A to 41E lying inner edge surfaces and the pins 41A to 41E with the bearing plates 44A to 44E store on the surface.

This in the first storage section 50A arranged first bearing plate 44 A is between a first block side bearing portion 51A the cylinder block 5 and a first bearing cap 52A attached to the first block side bearing section 51A is coupled. This in the second storage section 50B arranged second bearing plate 44B is between a second block side bearing section 51B from cylinder block 5 and a second bearing cap 52B attached to the second block side bearing section 51B is coupled. This in the third storage section 50C arranged second bearing plate 44C is between a third block side bearing portion 51C the cylinder block 5 and a third bearing cap 52C attached to the third block side bearing section 51C is coupled. The fourth storage section 50D arranged fourth bearing plate 44D is between a fourth block side bearing section 51D of the cylinder block 5 and a fourth bearing cap 52D attached to the fourth block side bearing section 51 D is coupled. The fifth bearing section 50E arranged fifth bearing plate 44E is between a fifth block side bearing portion 51E of cylinder block 5 and a fifth bearing cap 52E attached to the fifth block side bearing section 51E is coupled.

As in 8th are the block side bearing sections 51A to 51E Partition walls, the crank chambers 53A to 53D form each of the first to fourth cylinders 1 to 4 match that in the cylinder block 5 are shaped and according to the cones 41A to 41E spaced in the cylinder bank direction. In the present example, the block side storage sections correspond 51A to 51E the journal bearing wall sections according to the present invention, and the bearing caps 52A to 52E correspond to the shaft-bearing profiles according to the present invention.

The respective bearing plates 44A to 44E consist of an arcuate upper plate and an arcuate lower plate. Together, the upper and lower plates form a cylindrical shape (see 3 and 4 ). In addition, the bearing plates 44A and 44E each between one on the corresponding bearing caps 52A to 52E formed arcuate surface and one on the corresponding bearing caps 52A and 52E formed arcuate surface and between the two upper and lower sides of the block side bearing portions 51A and 51E and the bearing caps 52A and 52E inserted.

Continue, like 3 and 4 show are the respective bearing caps 52A to 52E each by a bolt 47 to the block side bearing sections 51A coupled to 51E, on both sides of the corresponding pin 41A to 41E. Specific is a pair of threaded holes 55 on both sides of the arcuate surfaces (bearing surfaces of the corresponding bearing plates 44A 44E) forming the lower surfaces of the respective block side support portions 51A to 51 E represent. In addition, when the bolt 47 from below through one of the respective bearing caps 52A to 52E formed through hole and guided in hole 55 is screwed, are the corresponding bearing cap 52A to 52E each to the block side storage sections 51A to 51E coupled.

Although a detailed description will be made later, this is a first oil feed path 68A up to a fifth oil supply path 68E , respectively the bearing sections 50A to 50E at locations of the corresponding block side bearing sections 51A to 51E Add oil, in the cylinder block 5 shaped t (see 5 and 6 ).

As in 2 to 4 is a circumferential oil groove 45 provided, which stores oil through the respective oil supply paths 68A to 68E is supplied, and an oil supply hole 45a for receiving the oil for the oil groove 45 is at an inner edge surface of the upper plate of the respective bearing plates 44A to 44E shaped.

In addition, a first inner oil path 46A , a second inner oil path 46B and a third inner oil path 46C integral and communicative in the crankshaft 12 formed, from the first crank pin 43A , from the first crank arm 42A , the second pin 41B and the second crank arm 42B to the second crank pin 43B , Similarly, a first inner oil path 47A , a second inner oil route 47B and a third inner oil route 47C integral and communicative in the crankshaft 12 shaped, namely by the fourth crank pin 43D , the fourth crank arm 42D , the fourth pin 41D and the third crank arm 42C until the third crank pin 43C , In the given example the internal oil paths correspond 46A to 46C and 47A to 47C the internal passes of the present invention.

A first inner oil route 46A penetrates the second pin 41B in the direction of diameter and communicates with the oil groove 45 , The second inner oil way 46B , the first inner oil route 46A branched off, opens into an outer edge surface of the first crank pin 43A , and the third inner oil path 46C, that of the first inner oil path 46A branched out, opens into an outer edge surface of the second crank pin 43B (please refer 2 ). The other first inner oil route 47A penetrates the fourth cone 41D in the direction of diameter and communicates with the oil groove 45 , In addition, the second inner oilway opens 47B , the first inner oil route 47A is branched off, on an outer edge surface of the fourth crank pin 43D , and the third inner oil route 47C , the first inner oil route 47A branched off, opens into an edge surface of the third crank pin 43C (please refer 2 ).

In other words, the inner ones in front of the crankshaft 12 located oil paths 46A to 46C lead oil, the second bearing section 50B with the second bearing plate 44B through the second oil supply path 68B is supplied to the first crank pin 43A who is the first connecting rod 11A stores, and the second crank pin 43B who is the second connecting rod 11B outsourced. On the other hand, the internal oil routes lead 47A to 47C behind the crankshaft 12 lie, oil to fourth storage section 50D with the fourth bearing plate 44D through the fourth oil supply path 68D to the fourth crank pin 43D who is the fourth connecting rod 11D stores and to the third crank pin 43C who has the third connecting rod 11C outsourced.

<Description of the oil supply device>

Hereinafter, the oil supply device 1 for the oil supply (operating oil) to respective operating ranges of the engine 2 in detail regarding drawing 6 described. The "hydraulic operating ranges" refer to devices (the HLA 24 , the VVT 33 and the like) which are operated by receiving oil pressure or oil pressure at oil supply portions (the oil nozzles 28 and 29, the oil supply portions 30 and 31 and the like) that supply oil by applying oil pressure to substances such as lubricating oil or cooling oil.

As shown, the oil supply device contains 1 an oil pump 56 caused by rotation of the crankshaft 12 is driven, and an oil supply path 60 , with the oil pump 56 is connected and pressurized oil the corresponding hydraulic operating ranges of the engine 2 supplies. Furthermore, the oil pump 56 one from engine 2 driven auxiliary machine.

The oil pump 56 According to the present embodiment is a known variable displacement oil pump. The oil pump 56 comprising: a housing 561 formed of a pump body having a C-shaped portion so as to open one end side and having inside a pump housing chamber consisting of a columnar space and a cover profile covering the opening of the pump body; a drive shaft 562 rotating through housing 561 is mounted, which penetrates into an approximately central part of the pump housing chamber and rotating by crankshaft 1 is stored; a pump element consisting of a rotor 563 and rotatably supported within the pump housing chamber and having its central portion coupled to the drive shaft and blades 564 , each housed retractable in a plurality of radially cut slots and in an outer edge region of the rotor 563 are shaped; a cam ring 566 , which in relation to the center of rotation of the rotor 563 is arranged eccentrically on an outer peripheral portion of the pump element and pump chambers 565 forms, which represent several operating oil chambers, together with the rotor 563 and the adjacent leaves 564 ; a feather 567 , which is housed as a taut profile in the pump body and the cam ring 566 constantly under tension in one direction, in which a certain eccentricity of the cam ring 566 with respect to the center of rotation of the rotor 563 increases: and a pair of ring profiles 568 conducting at both side portions of an inner peripheral surface of the rotor 563 is arranged and has a smaller diameter than the rotor 563 , The housing 561 includes an inlet 561a, which is the inner pumping chamber 565 Supplying oil, and an outlet opening 561b , the oil from the pump chamber 565 discharges. A pressure chamber 569 coming from an inner edge of the case 561 and an outer peripheral surface of the cam ring 566 is formed inside the housing 561 shaped, and the housing 561 contains a feed hole 569a in the pressure chamber 569 empties. In other words, the oil pump 56 is configured so that when oil enters the pressure chamber 569 is introduced through the supply hole 569a, the cam ring 566 around a lifting point 561c pivots, the rotor 563 in relation to the cam ring 566 is relatively eccentric, and the output varies.

One of the oil pan 7 facing oil screen 57 is with inlet 561a the oil pump 56 coupled. An oil strainer 58 and an oil cooler 59 are upstream in sequence in an oil path 61 arranged with the outlet opening 561b the oil pump 56 communicated. The in oil sump 7 stored oil is from the oil pump 56 through the oil strainer 57 pumped, in the oil filter 58 filtered, in the oil cooler 59 cooled, and then the main channel (described below) 64 in cylinder block 5 fed. Furthermore, in 5 for a better overview the oil pump 56 and the oil pan 7 separate from engine 2 shown.

An oil route 62 , the oil from the main channel 64 to the pressure chamber 569 the oil pump 56 leads, is with the oil pump 56 connected. A second (hereinafter described) consisting of a linear solenoid valve oil control valve 93 is between the oil route 62 and the main channel 64 arranged. A capacity of the oil pump 56 changes when an oil flow rate (an oil pressure) in the pressure chamber 569 through the second oil control valve 93 will be changed.

The oil supply path 60 is made up of passes in the cylinder head 4 , in the cylinder block 5 , in the crankcase 6 and the like, and tubes. Furthermore, in the following description, the cylinder head 4 , the cylinder block 5 and the crankcase 6 as a main engine body, if so.

As in 5 and 6 shown, belong to the oil supply path 60 : the upstream main channel 64 primarily serving to supply the required oil to the high pressure hydraulic operating areas; the two downstream tributaries 65 and 66 that deliver oil to the hydraulic operating areas that need relatively lower pressure (hydraulic operating areas where the required pressure is lower than where the oil is supplied directly from the main channel); the oil route 61 for the oil supply, the oil from the oil pump 56 to the main channel 64 over the oil filter 58 and the oil cooler 59 promotes; the oil route 62 , the oil from the main channel 64 derived and pump control to the pressure chamber 569 the oil pump 56 supplies; as well as different oil ways, from the main channel 64 and the like branch off.

The oil route 61 contains: a pipe 61a that the outlet opening 561b the oil pump 56 and an opening part of the crankcase 6 together links; a passage 61b molded in the main engine body to the oil cooler 59 reach on a side surface (an inlet side surface) of the cylinder block 5 is attached - from the opening part via oil filter 58 at a side portion (an inlet side surface) of the crankcase 6 is attached; and a passage 61c who has the oil cooler 59 and the main channel 64 connects with each other.

As in 1 and 5 represented, is the main channel 64 in the cylinder block 5 arranged at a location which is farther out (closer to the inlet side) than the cylinder bore 8th in the direction of the width of the cylinder block 5 and those near a lower end portion of the cylinder bore 8th lies. The main channel 64 leads in the direction of the cylinder bank. The secondary channels 65 and 66 (as the first secondary channel 65 and second side channel 66 are designated) in each cylinder block 5 opposite the main canal 64 arranged, with the cylinder bore 8th as the middle, so the second secondary channel 66 further out in the direction of the width of the cylinder block 5 is located (closer to a side opposite the cylinder bore 8th ) as the first secondary channel 65 , The secondary channels 65 and 66 are at prescribed intervals in the width direction of the cylinder block 5 intended. The corresponding channels 64 to 66 including the main channel 64 run horizontally in a straight line in the direction of the cylinder bank, ie parallel to each other.

Oil supply paths, each from the main channel 64 and the first secondary channel 65 branch off and the oil to the bearing sections 50A to 50E lead, are in cylinder block 5 shaped.

Specifically, as in 5 and 6 1, the first oil supply path 68A becomes the third oil supply path 68C and the fifth oil supply path 68E , each from the first secondary channel 65 branch off and the first storage section 50A reach, the third storage section 50C , and the fifth bearing section 50D in the cylinder block 5 shaped. Furthermore, the second oil supply path 68B and the fourth oil supply path 68D , each from the main channel 64 branch off and the second bearing section 50B reach, as well as the fourth storage section 50D in cylinder block 5 shaped. In the present example, the oil supply paths 68A, 68C and 68E correspond to the first branch oil paths according to the present invention, and the oil supply paths 68B and 68D correspond to the second branch oil paths according to the present invention.

As in 8th and 9 is shown, the first Ölzufuhrweg 68A in the first block side bearing section 51A of the cylinder block 5 shaped. The first oil supply path 68A branches off the second secondary channel 66 in the position of the first block side bearing section 51A towards the cylinder bank and runs diagonally from the second secondary channel 66 to the first storage section 50A , Besides, as in 3 shown, opens the first Ölzufuhrweg 68A the arcuate surface of the first block side bearing portion 51A , the first bearing plate 44A in a position opposite to an outer edge surface of the first bearing plate 44A supports. Accordingly, oil becomes the oil groove 45 of the first bearing plate 44A from the first secondary channel 65 through the first oil supply path 68A guided. Furthermore, the oil supply hole 45a of the first bearing plate 44A in a position opposite to the first oil supply path 68A shaped.

Although not shown, the third oil supply path becomes 68C in the third block side bearing section 51C shaped similar to the first Ölzufuhrweg 68A , and the fifth oil supply path 68E becomes the fifth block side bearing section 51E shaped in a similar way. Furthermore, reference sign means 54 in 9 and 10 one at the block side bearing sections 51A to 51E shaped opening, and the adjacent crank chambers 53A to 53D communicate with each other through the opening 54 ,

On the other hand, as in 8th and 10 As shown, the second oil supply path 68B is in the second block side storage portion 51B of the cylinder block 5 shaped. The second oil supply path 68B branches off the main channel 64 at a location of the second block side bearing section 51B towards the cylinder bank and runs diagonally downwards from the main channel 64 in the direction of the second bearing section 50B , In addition, as in 4 illustrated, the second Ölzufuhrweg opens 68B at the arcuate surface of the second block side bearing portion 51B , the second bearing plate 44B at a location opposite to an outer edge surface of the second bearing plate 44B outsourced. Therefore, the oil groove 45 of the second bearing plate 44B from the main channel 64 through the second oil supply path 68B Supplied with oil. Furthermore, the oil supply hole 45a of the second bearing plate 44B at a location opposite the second oil supply path 68B shaped.

Although not shown, the fourth oil supply path 68D in the fourth block side bearing section 51D shaped in a similar manner as the second oil supply path 68B ,

A relay oil path 70 for connecting the main channel 64 and the side channels 65 and 66 together in the direction of width of the cylinder block 5 , as in 4 and 10 is further formed in the second block side support portion 51B. As shown, the relay oil path continues 70 as follows: a grooved oil path 69a , in a peripheral direction along an outer edge surface of the second bearing plate 44B extending, whose end portion with the second oil supply path 68B communicating; and an oil route 69b communicating with oil path 69a at the other end portion thereof diagonally upward from the other end portion of the oil path 69a in the direction of the first secondary channel 65 which runs at a point slightly below the first secondary channel 65 turns, at a point under the second secondary channel 66 passes and on an outlet side surface of the cylinder block 5 empties.

One OCV unit (oil control valve) 90 is attached to an area which the exhaust side surface of the cylinder block 5 and from the second block side bearing section 51B to the first block side storage section 51A is enough (see 5 . 7 , and 8).

As in 10 and 11 are two oil control valves, namely the first and second oil control valves 92 and 93 in the OVC unit 90 accommodated. As shown only schematically, is the first oil control valve 92 with the first secondary channel 65 and the second sub-channel 66 via relay oil ways 65a and 66a connected, each in the cylinder block 5 are shaped, and with the main channel 64 over the relay oil path 70 and the second oil supply path 68B connected. The second oil control valve 93 is with the main channel 64 over the relay oil path 70 connected and to the oil route 62 connected (an oil supply path that supplies oil to the discharge amount of the oil pump 56 to regulate) in cylinder block 5 is shaped. Accordingly, the main channel communicates 64 each with the first secondary channel 65 and the second sub-channel 66 over the relay oil path 70 , the first oil control valve 92 and the relay oil ways 65a and 66a communicate with oil route 62 over the relay oil path 70 and the second control valve 93 , Furthermore, in the present example, the relay oil path corresponds 70 the first relay oil path according to the present invention, and the relay oil paths 65a and 66a correspond to the second relay oil path according to the present invention.

As in 1 and 8th shown are the first crank chamber 53A to the fourth crank chamber 53D corresponding to the respective cylinders 1 to 4 correspond between the block side bearing sections 51A to 51E in cylinder block 5 lie against each other, shaped. As already described and in 1 and 5 are shown, the nozzle mouthpieces 28a the oil nozzles 28 for the piston cooling in ceiling sections of the corresponding crank chambers 53A to 53D in places under the main canal 64 attached, and the corresponding nozzle mouthpieces 28a are with the main channel 64 connected. In addition, the nozzle mouthpieces 29a the oil nozzles 29 for piston lubrication in ceiling sections of the corresponding crank chambers 53A to 53D in places under the second secondary channel 66 attached, and the corresponding nozzle mouthpieces 29a are with the second secondary channel 66 connected.

As in 1 . 7 8 and 8 are the nozzle mouthpieces 28a and 29a of the corresponding oil nozzles 28 and 29 arranged so that the nozzle mouthpieces 28a and 29a - in a condition in which the nozzle mouthpieces 28a and 29a approximately the ceiling sections of the corresponding crank chambers 53A to 53D follow - from positions outside the cylinder bore 8th to positions below the cylinder bore 8th can run, and that the tips of the nozzle mouthpieces against pistons 9 are directed.

As in 5 and 6 shown, the main engine body also contains a branch oil path 72 that of an end portion on one side of the first cylinder 1 of the main channel 64 of the cylinder block 5 branches off and to the cylinder head 4 runs. The branch oil path 72 serves to deliver operating oil to the VVT described above.

In addition, the main engine body includes a branch oil path 73 that of an end portion on one side of the first cylinder 1 from the first secondary channel 65 branches off and to the cylinder head 4 leads. An oil route 74 in the cylinder head 4 leading in the width direction is with the branch oil path 73 connected. An oil route 75 which runs horizontally toward a cylinder bank at a predetermined position on an intake side in the cylinder, and an oil path 76 , which runs horizontally in the direction of the cylinder bank at a predetermined position on the exhaust side in the cylinder head 4, branches from the oil path 74 from. Between the oil ways 75 and 76 the inlet side HLA communicates 24 with the inlet side of Ölweg 75 , and a nozzle tip of an oil supply section (not shown) for lubricating a cam pin of the exhaust-side camshaft 20 communicates with the exhaust side oil path 75 via the branch oil path 75a , Similarly, the outlet HLA communicates 24 with the outlet side oil path 76 , and a nozzle tip of an oil supply section (not shown) for lubricating a cam pin of the intake-side camshaft 21 communicates with the exhaust side oil path 76 over a branch oil way 76a ,

An upper end of the branch oil route 73 of the first secondary channel 65 runs to the camshaft cover 3 , and the nozzle mouthpiece 30a of the oil supply section 30 , the lubricating oil to the inlet-side swivel arm 22 leads, and the nozzle mouthpiece 31a of the oil supply section 31 , the lubricating oil to the exhaust side swivel arm 23 leads, communicate with the branch oil path 73 over (not shown) oil paths.

In addition, an oil pressure sensor 80 that the oil pressure in the main channel 64 detects near an end section of the main channel 64 on the side of the first cylinder 1 connected, and a signal about the oil pressure of the main channel 64 is from Oil pressure sensor 80 to the controller (described below) 100 sent when engine 2 running.

Further (not shown) drop lubricating oil and cooling oil, which are fed to the cam pin, which rotating the camshaft 20 and 21 store, as well as the bearing plates 44A to 44E rotating the crankshaft 12 store the flask 9 , the camshafts 20 and 21 and the like, down into the oil pan 7 through a drain oil path (not shown) after the cooling or lubrication is completed, and this oil is then removed from the oil pump 56 circulated again.

Operating functions of the engine 2 like the ones described above are from the controller 100 controlled. The controller 100 is a known microcomputer-based control device that controls the oil pressure in the oil supply path 60 integral controls. Information from various sensors, which indicate the operating conditions of the engine 2 recognize, be in the controller 100 entered. That's the way the engine points 2 For example, in addition to the oil pressure sensor 80, a crank angle sensor 81 on, the rotation angle of the crankshaft 12 detects, as well as an air flow sensor 82 that by engine 2 intake air volume detects, an oil temperature gauge 83 that the oil temperature in oil supply path 60 detects a cam angle sensor 84 , which is the rotational phases of the camshafts 20 and 21 detects, and a water temperature sensor 85 , which is the temperature of the cooling water in engine 2 detects, and the measurement data of these sensors 80 to 85 become the controller 100 fed. The controller 100 detects the engine speed based on the measurement data of the crank angle sensor 81 , detects the engine load due to the measurement data of the air flow sensor 82 and detects an operating angle of the VVT based on the measured data of the cam angle sensor 84 ,

Because of the respective sensors 80 to 85 detected information determines the controller 100 an operating condition of the engine 2 , sets a target oil pressure based on a given map and provides feedback control with respect to the oil pressure in the oil supply path 60 based on the target oil pressure.

More specifically, the oil supply device provides 1 Oil to a variety of hydraulic operating ranges (VVT, HLA 24 , the oil nozzles 28 and 29 , the oil supply sections 30 and 31 and the like), by oil pump 56 to be served. The oil pressure required for the respective hydraulic operating ranges varies depending on the operating state of the engine 2 , So that all hydraulic operating ranges in all operating conditions of the engine 2 can obtain the required oil pressure, it is rational, for each operating condition of the engine 2 set the oil pressure to meet the maximum demand of the respective operating ranges at least, and this demand as the respective target engine oil pressure 2 use. For this to happen, the target oil pressure of the individual oil supply sections (in other words, the second oil supply path 68B and the fourth oil supply path 68D ) or the like, responsible for the hydraulic operating ranges requiring a relatively high oil pressure; in the present embodiment, these are the VVT, the oil nozzles 28 and 29 , and the second and fourth bearing sections 50B and 50D , and in this case, an oil discharge amount of the oil pump 56 be controlled so that it corresponds to the target oil pressure. Of course, the target oil pressure generated in this way also meets the needs of the other hydraulic operating ranges, which require a relatively low oil pressure.

Although not shown, in the present embodiment, for each operating state of the engine 2 set an oil pressure control map in which the target oil pressure of the operating state is set after the highest required oil pressure of the oil pressure of the feed sections and the like, for the VVT, the oil nozzles 28 and 29 as well as the second and fourth bearing plates 44B and 44D is responsible in the memory section of the controller 100 are stored. The controller 100 creates oil pressure feedback control, with a pump output of the oil pump 56 from a function of the second oil control valve 93 is regulated, so that oil pressure (the actual oil pressure) of the main channel 64 as from the oil pressure sensor 80 detected represents the target oil pressure.

Furthermore, the first oil control valve 92 configured so that it alone the oil flow rates of the first secondary channel 65 and the second subsidiary channel 66 Interlocking rules. By the controller 100 the first oil control valve 92 according to an operating condition of the engine 2 regulates, he regulates the oil pressure, that of the first secondary channel 65 to the bearing plate 44A , the third bearing plate 44C and the fifth bearing plate 44F through the first oil supply path 68A , the third oil supply path 68C and the fifth oil supply path 68 and the controller controls an oil flow rate with respect to the second sub-channel 66 to the oil injection through oil nozzle 29 for the piston lubrication on and off.

The first oil control valve 92 consists eg of a linear solenoid valve, and the controller 100 regulates one to the corresponding bearing plates 44A oil quantity supplied up to 44E, the on and off states of the oil nozzle 28 and the like (as in 12 shown) by a duty control signal to the first oil control valve 92 is sent. Furthermore, there is the second oil control valve 93 similarly, for example, from a linear solenoid valve, and by transmitting a duty control signal to the second oil control valve 93 regulates the controller 100 one from oil pump 56 delivered amount of oil.

<Operational advantage of the oil supply device 1 >

In the above-described oil supply device 1 gets out of the oil pump 56 ejected oil in the oil filter 58 filtered, in the oil cooler 59 cooled and over oil route 61 in the main channel 64 in the cylinder block 5 introduced. Thereafter, a part of the oil from the nozzle mouthpiece 28a the oil nozzle 28 for cooling the piston 9 and another part of the oil is the second bearing part 50B and the fourth storage section 50D the crankshaft 12 through the second oil supply path 68B and the fourth oil supply path 68D fed and continue to the corresponding crank pins 43A to 43D through the inner oil ways 46A to 46C and 47A to 47C of the crankshaft 12 fed. In addition, oil is in the main channel 64 from the second oil supply path 68B to the first secondary channel 65 and to the second bypass channel 66 through the relay oil path 70 , the first oil control valve 9 and the relay oil ways 65a and 66a fed and at the same time the VVT 33 over the oil route 72 fed from the main channel 64 branches.

That the first secondary channel 65 supplied oil is the first storage section 50A , the third storage section 50C and the fifth bearing section 50E the crankshaft 12 through the first oil supply path 68A , the third oil supply path 68C and the fifth oil supply path 68E fed. Furthermore, a part of the first secondary channel 65 supplied oil to the cylinder head 4 through the branch oil path 73 supplied by the first secondary channel 65 branches off and continues the HLA 24 through the oilways 75 and 76 fed and at the same time the cam pin parts of the camshafts 20 and 21 through branch oil ways 75a and 76a fed, each from the oil paths 75 and 76 branch. Furthermore, the oil from the corresponding nozzle mouthpieces 30a and 31a the oil supply sections 30 and 31 the swivel arms 22 and 23 through the branch oil path 73 fed.

The second secondary channel 66 supplied oil is from the nozzle mouthpiece 29a the oil nozzle 29 injected to the piston 9 to lubricate.

In the oil supply device 1 , are the first secondary channel 65 and the second sub-channel 66 , each extending in the direction of the cylinder bank, in a side portion (outlet side) of the cylinder bore 8th of the cylinder block 5 intended. The following advantages are achieved in that the first secondary channel 65 for the oil supply to crankshaft 12 (the first, third and fifth bearing sections 50A . 50C and 50E ) are arranged on an inner side, in other words, that one side of the cylinder bore 8th and the second sub-channel 65 for the supply of oil to the oil nozzle 29 on an outside of the first secondary channel 65 lie:

First, as in 9 and 10 shown, the oil supply paths 68A , 68C and 68E, from the first secondary channel 65 branch off, near the cylinder bore 8th be arranged because the first secondary channel 65 on the side of the cylinder bore 8th lies. As a result, the screw hole 55 for fixing the bearing caps 52A . 52C and 52E at the block side bearing sections 51A . 51C and 51E be arranged with clearance at a location that of the oil supply paths 68A . 68C and 68E is separated on an outside (on one side off the cylinder bore 8th ). Usually the screw hole 55 and the oil supply routes 68A . 68C and 68E edited after the cylinder block 5 has been molded as a cast profile of aluminum alloy or the like. Because the screw hole 55 However, as described above can be arranged with margin, editing errors can - for example, that the screw hole 55 and the oil supply routes 68A . 68C and 68E communicate with each other - avoid it from the beginning.

Furthermore, because - because the second secondary channel 66 on an outside of the first secondary channel 65 is arranged - the nozzle mouthpiece 29a the oil nozzle 29, which is connected thereto, receive a shape which is almost on the ceiling surface of the crank chamber 53 runs, and which, as described above, only slightly deviates from the vertical direction (see 1 ). That's why the nozzle mouthpiece 29a be arranged in a compact manner while interfering contact between the crank webs 42 ( 42A to 42D ) of the crankshaft 12 and the nozzle tip 29a in the tight crank chambers 53 ( 53A to 53D) is avoided.

Furthermore, according to the above-described configuration of the oil supply device 1 , lies the main channel 64 at a point opposite the first secondary channel 65 relative to the cylinder bore 8th and oil becomes the bearing portions except the first, third and fifth bearing portions 50A , 50C and 50E of the crankshaft 12 fed, or in other words, the second bearing section 50B and the fourth storage section 50D lead through the second oil supply path 68B and the fourth oil supply path 68D coming from the main channel 64 branch. According to this configuration, oil can, as it is with relatively high pressure from the oil pump 56 to the second storage section 50B and the fourth storage section 50D can be delivered, even without excess or lack of the second and fourth storage sections 50B and 50D be delivered while the appropriate amounts of oil to the appropriate crank pins 43A to 43D the crankshaft 12 to be delivered. On the other hand, the supply of an excess amount of oil to the first, third and fifth bearing sections 50A , 50C and 50E are prevented by passing the oil at a relatively low pressure through the oil supply paths 68A . 68C , and 68E is guided by the first secondary channel 65 and therefore adequate quantities of oil can be supplied without surplus or deficiency. That is why it is in relation to the oil supply device 1 also an advantage that the crankshaft can be lubricated properly.

While the cylinder block 5 with respect to the above-described oil supply device 1 For example, is cast from an aluminum alloy or the like, the die casting has prevailed in recent years. As the following simple overview shows, a die-cast is made with a cylinder block 5 prepared cavity (preparation stage) by molten metal such as an aluminum alloy, is poured into the cavity of the mold to form the cylinder block (molding stage). In this case, the corresponding channels 64 to 66 poured, wherein previously core pins were arranged in the main body of the mold. Then, after the opening, the cylinder block becomes 5 finished as a product by reworking (drilling and pressing) (reworking step).

In this die-cast cylinder block 5 In the casting stage, the molten metal is poured into the cavity in the position defining an end portion of the casting on the side of the main channel 64 in the direction of cylinder block width 5 forms and the lower end portion of a side wall (a lower base part) of the crank chambers 53 ( 53A to 53D ) corresponds. In cylinder block 5 For example, this position is indicated by an arrow in 10 shown.

According to this method, since the molten metal is poured from one side of the cavity into the cavity having less core pins for forming the oil paths (the main oil supply path, the first subsidiary oil supply path, and the second subsidiary oil supply path), the flow of the molten metal is expected to become less disturbed by the core pins, and the flow behavior is improved. Therefore, the occurrence of voids can be suppressed, and the production yield can be effectively increased.

<Other configurations>

The above-described oil supply device 1 FIG. 14 is an example of a preferred embodiment of the engine oil supply apparatus according to the present invention, and a specific configuration may be modified as needed without departing from the gist of the present invention.

So are VVT, HLA 24 , the oil nozzles 28 and 29 , the oil supply sections 30 and 31 and the like associated with the oil supply path 60 Examples of hydraulic operating ranges according to the present invention and specific types of hydraulic operating ranges and specific connecting positions of the hydraulic operating range on the oil supply path 60 are not limited to the examples described in the above-described embodiment.

In addition, although one of engine 2 driven pump is requested in the embodiment described above as a protected object, the oil pump 56 alternatively be driven by an electric motor.

Further, although an example is described in which the present invention is applied to a four-cylinder in-line gasoline engine, the present invention may also refer to other engines such as a diesel engine.

The present invention described above can be summarized as follows:

Specifically, the present invention relates to an engine oil supply apparatus including: a cylinder block including a plurality of journal-bearing wall portions aligned in a cylinder bank direction and supporting, respectively, a crankpin of a crankshaft and a cylinder communicating with a crank chamber formed between the journal-bearing abutting wall portions; a shaft-bearing profile, which is arranged on the journal-bearing wall portion and the crank pin is in communication with the crankpin-bearing wall portion; and a nozzle mouth fixed to a ceiling portion of the crank chamber and injecting oil into a piston sliding in the cylinder, the cylinder block having a first oil supply path extending at a position on a side portion of the cylinder toward the cylinder bank perpendicular to the cylinder bank direction is; a branch oil path branched from the first oil supply path at a position of the journal bearing wall portion that supplies oil to a crank bearing portion that supports the crankpin and a second oil supply path that extends at a location toward the cylinder bank that is farther outside than the first oil supply path Direction width, and supplies the nozzle mouthpiece with oil.

According to this configuration, the branch oil path branching from the first oil supply path can be located closer to the cylinder because the first oil supply path for supplying oil to the crank bearing section (branch oil path) is closer to one side Cylinder is the second oil supply path in the cylinder block width direction. Since the bore portions for mounting parts such as the screw hole for assembling the shaft-supporting profiles with the journal-bearing wall portion on an outer side (which separates from the cylinder) of the branch oil path can be arranged with margin, processing errors in the processing of the branch oil path and in the attachment of Avoid drilling - such as making a wrong connection between the branch oil path and the mounting holes - from the outset. In addition, since the nozzle tip can be shaped to face the inside of the cylinder, namely, approximately along the ceiling surface of the crank chamber, because the second oil supply path for supplying oil to the nozzle tip, namely at a position separate from the cylinder, can Nozzle mouthpiece can be arranged in a compact manner in the ceiling portion of the crank chamber, thereby preventing it interferes with the crankshaft and in particular with the crank arm (the crank weight) in conflict.

In the oil supply apparatus, preferably, the crankshaft includes a plurality of crankpins, and oil is introduced into the crankshaft from a specific crankpin among a plurality of crankpins and supplied to a crankpin through an inner passage formed in the crankshaft, the first and second oil supply paths being the first sub-oil supply paths, respectively second sub-oil supply path are defined, and the branch oil path is defined as a first branch oil path; the cylinder block includes a main oil supply path extending toward the cylinder bank at a position opposite to the first subsidiary oil supply path in the width direction, the cylinder being the center, and the oil coming from an oil pump being introduced; and a second branch oil path branching from the main oil supply path at a position where the journal bearing wall section is located, supplying oil to the crank bearing section from which the specific crankpin is stored supplying the first subsidiary oil supply path and the second subsidiary oil supply path to a downstream side of the main oil supply path Oil flow direction is connected, wherein the first branch oil path to the crank bearing portion of the crank pin provides that does not represent the specific crank pin.

According to this configuration, appropriate quantities of oil may preferably be supplied to the corresponding crankpins and crankpins of the crankshaft. In addition, since the main oil supply path and the sub oil supply path are separated from each other on both sides of the cylinder, in the production (die casting) of the cylinder block, voids formation can be suppressed, which frequently causes the oil paths to be inadvertently connected.

In this case, preferably, the oil supply device includes a relay oil path that constitutes an oil supply path for connecting the first sub-oil supply path and the second sub-oil supply path to the main oil supply path, and which is formed on a journal-bearing wall section at which a second branch oil path is formed under a plurality of journal-bearing wall sections. and further connected to the second branch oil path.

According to this configuration, the main oil supply path and the first sub-oil supply path or the second sub-oil supply path can communicate efficiently with each other by using a journal-bearing wall section without the first branch oil path among the plurality of journal-bearing wall sections or the second branch oil path.

In this case, it is preferable that when the relay oil path is defined as a first relay oil path, the oil supply device includes an oil control valve that includes at a side surface of the cylinder block in the width direction and a second relay oil path that is formed on the journal bearing wall portion, and causes First Nebenölzufuhrweg or the second Nebenölzufuhrweg communicates with the oil control valve and the first relay oil path is formed so that it communicates with the oil control valve.

According to this configuration, the productivity of the cylinder block is increased because the first and second relay oil paths may have relatively simple shapes that open on the side surface of the cylinder block and also cause the main oil supply path to communicate with the first or second sub oil supply paths via the oil control valve.

In addition, the present invention is a method for producing the cylinder block used in the above-described oil supply apparatus, the method comprising the steps of: a preparation stage for preparing a mold having a cavity corresponding to the cylinder block; a mold stage for molding the molten metal in the cavity of the mold, the metal in the mold stage being from a position representing an end portion of the mold on the side of the oil supply path in the cylinder block width direction and corresponding to the lower end of a sidewall of the crank chamber.

According to this method, in which the molten metal is poured into the cavity from a side of the cavity having a smaller number of core pins for forming the oil paths (the main oil supply path, the first oil supply path, and the second subsidiary oil supply path), the running properties can be improved the occurrence of voids can be suppressed.

Claims (4)

An engine oil supply apparatus comprising: a cylinder block (5) including a plurality of journal-bearing wall portions (51A to 51E) aligned in a cylinder bank direction and supporting a crankpin (41A to 41E) of a crankshaft (12) and a cylinder (8), respectively; communicating between the juxtaposed journal-bearing wall sections (51A to 51E) formed crank chamber (53); a shaft-supporting profile (52A to 52E) provided on the journal-bearing wall portion (51A to 51E) and supporting the crankpin (41A to 41E) of the crankshaft (12), and communicating with the journal-bearing wall portion (51A to 51E) ; and a nozzle orifice (29a) attached to a ceiling portion of the crank chamber (53) and supplying oil to a piston (9) which slides in the cylinder (8), the cylinder block (5) including a first oil supply path (65) Toward the cylinder bank at a position on a side portion of the cylinder (8) in the widthwise direction which is perpendicular to the cylinder bank direction; a branch oil path (68A, 68C, 68E) branched from the first oil supply path (65) at a position of the journal supporting wall portion (51A to 51E) and supplying oil to a crank bearing portion (50A to 50E) on which the crank journal (41A to 41E) is supported is; and a second oil supply path (66) extending in a direction of the cylinder bank at a location farther outside than the first oil supply path (65) in the width direction and supplying oil to the nozzle mouthpiece (29a), characterized in that the crankshaft (12 ) includes a plurality of crankpins (41A to 41E), and oil is supplied from a specific crankpin (41B, 41D) among the plurality of crankpins (41A to 41E) of the crankshaft (12) and a crank pin (43A to 43D) a passage (46A-46C, 47A-47C) formed inside the crankshaft (12) is defined, wherein the first oil supply path (65) and the second oil supply path (66) are respectively defined as a first sub-oil supply path and a second sub-oil supply path, and the branch oil path ( 68A, 68C, 68E) is defined as a first branch oil path (68A, 68C, 68E), the cylinder block (5) includes a main oil supply path (64) to be fed toward the cylinder bank at a position opposite to the first subsidiary oil forward (65) side, the cylinder (8) being the center and supplied to the oil discharged from an oil pump (56), and a second branch oil path (68B, 68D) extending from the main oil supply path (64). branches off at a location of the journal bearing wall portion (51B, 51D) and supplies oil to the crank bearing portion (50B, 50D) at which the specific journal (41B, 41D) is supported; the first sub oil supply path (65) and the second sub oil supply path (66) are connected to a downstream side of the main oil supply path in the oil flow direction, and the first branch oil path (68A, 68C, 68E) supplies oil to the crank bearing section (50A, 50C, 50E) of the crank pins (41A , 41C, 41E) except the specific crankpin (41B, 41D). Engine oil supply device according to Claim 1 characterized in that it further comprises: a relay oil path (70) that is an oil supply path and that causes the first sub oil supply path (65) or the second sub oil supply path (66) to communicate with the main oil supply path (64) and the one on a journal bearing Wall portion (51 B) is formed, on which the second branch oil path (68 B) is formed, under the plurality of journal-bearing wall portions (51 A to 51 E), and further connected to the second branch oil path (68 B). Engine oil supply device according to Claim 2 characterized in that, when the relay oil path (70) is defined as a first relay oil path, the oil supply device includes an oil control valve (92, 93) attached to one face of the cylinder block (5) in the width direction, and a second relay oil path (65a 66a) fixed to the journal bearing wall portion (51B) and causing the first sub oil supply path (65) or the second sub oil supply path (66) to communicate with the oil control valve (92, 93), and the first relay oil path (70 ) is shaped so as to communicate with the oil control valve (92, 93). Process for the preparation of the in the engine oil supply device according to one of Claims 1 to 3 used cylinder block (5), characterized in that the method consists of: a preparation stage for preparing a mold with a cylinder block (5) corresponding cavity; and a molding step for molding the cylinder block (5) by pouring the molten metal material into the cavity of the mold, wherein in the molding step, the molten metal is poured into the cavity of the mold from a position located at one end of the main oil supply path side (64) lies in the direction of the width of the cylinder block (5) and which corresponds to a lower end portion of a side wall of the crank chamber (53).

Images